Governor mechanism



Oct. 16, 1951 J, 3 DALE 2,571,842

GOVERNOR MECHANISM Filed March 18, 1946 4 Sheets-Sheet l 6/ .93 i 36 66C 7 I 84 d 'ZJJ 2:; i j 5 X 9 za i Oct. 16, 1951 J. s. DALE 2,571,842

.GOVERNOR MECHANISM Filed March 18, 1946 4 Sheets-Sheet 3 Oct. 16, 1951J. s. DALE 2,571,342

GOVERNOR MECHANISM Filed March 18, 1946 4 Sheets-Sheet 4 Patented Oct.16, 1951 UNITED STATES PATENT OFFICE GOVERNOR MECHANISM Joseph S. Dale,Rockford, Ill. Application March 18, 1946, Serial No. 655,086

4' Claims.

This invention relates to governor mechanism and is particularlyapplicable to governors of the hydraulic type.

.An object of the invention is to provide a governor of simpleconstruction, capable of responding more quickly to speed changes andcorrecting such changes more rapidly than governors heretofore employed.A further object is to provide a governor structure in which improvedcontrol means are provided, regulating more accurately the flow ofpressure fluid to the servomotor. Yet another object is to provide anovel fluid control valve mechanism in which the force resulting fromdynamic unbalance is reduced to a minimum and is not transmitted to thespeeder spring and fly weights. Another object is to provide a governorstructure in which novel speed adjustment mechanisms and speed droopadjustment devices are provided. Yet another object is to provide aspring drive mechanism whereby effective rotation of the fly weights isaccomplished; while at the same time absorbing slight oscillations ofthe prime mover. Other specific objects and advantages will appear asthe specification proceeds.

The invention is illustrated, in preferred embodiments, by theaccompanying drawings, in which Figure ,1 is a perspective view ofgovernor mechanism embodying my invention; Figs. 2 and.2',

vertical sectional views, the section being taken as indicated at line2-2 of Fig. 1 but showing two different constructions; Figs. 3, 3' and3", transverse sectional views, the sections being taken as indicated atline 3-3 of Fig. 2' but showing three different constructions; Fig. 4, atransverse sectional view, the section being taken as indicated at line44 of Fig. 2'; Fig. 5, a broken view similar to Fig. 2' but showing amodified form of the invention; Fig. 6, a perspective view of'the maindrive shaft or ball head drive shaft employed; Fig. 7, a perspectiveview of a modified form of the valve sleeve employed; Fig. 8, a brokensectional view of'a drive shaft equipped with a spring drive member; andFig. 9, a transverse sectional view, the section being taken asindicated at line 9'9 of Fig. 8. Similar reference numerals are appliedto corresponding parts throughout the views. For example, correspondingparts in Fig. 2 are given prime numerals to show relationship tocorresponding parts in changes of the prime mover; and C, adjustmentmeans for controlling the load on the speeder spring under variousoperating conditions.

The casing A may be of any suitable construction. In the particularillustration given, I0 designates a base plate, II, a block or framestructure carried by the plate liLand I2, a dome structure resting uponthe body member I I. The dome member I2 is provided with a flange baseI3 through which screws I 4, Fig. 2', extend to secure the dome in placeon the block II, other screws M, Fig. 2', beingprovided to fasten thebase plate It to the block II. A gasket I5 may be provided between theflange structure It and the block II. Another gasket [5 is providedbetween the base plate l0 and the block II.

The block II may be formed of a solid piece of metal, or a coredcasting, having openings therethrough providinga pump chamber, shaftopenings, and conduits for the supply of fluids, etc.

The dome casing I2 is provided at its top with a shoulder II. A recessI6 is provided under the cap 9' (Fig.2), or the cap 9 (Fig. 2). In theconstruction shown in Fig. 2, the cap 9' is held to the dome l2 by capscrews. In the construction shown in Fig. 2, the cap 9 is threadedlyengaged to the dome I2. The casing I2 provides in its interior a chamberadapted to receive the fly weight mechanism, etc.

The control mechanism B may be of any suitable type or structure. In theillustration given, I provide a ball head I8, equipped with a reducedextension I9. In Fig. 2, a collar 2| is pressed on extension I9 andbears against shoulder II to retain the ball head IS in place. In Fig.2', the extension. I9 is tapped to receive a threaded bolt 20. Thebolt20 carries a flange 2| which rests upon the shoulder I'I, thusholding the ball head I8 in place. The fly weights 22 are secured totheball head I8 by the pivot pins 23 and are free toswing inwardly oroutwardly about pins 23. Each of the fly weights 22 is provided with anintegral arm 24 extending inwardly and equipped with a toe 25 turneddownwardly. The ball head I8 is provided with an integral key 26 forsecuring the ball head I8 to the ball head drive shaft 21.

The main drive shaft 21, which may also be referred to as the ball headdrive shaft, extends vertically through the casing members III and IIinto the dome l2, and is provided at its lower end witha slot 28suitable for connecting it to the driven part of the prime mover. Shaft21, therefore, rotates in synchronism with the driven part of the primemover. "Shaft 21 rotates in bore 33 and is provided near its lower endwith an integral gear member 29 which serves as a part of the gear pumpwhich will be later described. Above the gear 29, the block ll isprovided with outlet ports 30 leading to the sump of the prime mover orany other desired collection point for the pressure fluid, throughchamber 30 and passage 38*. Above the ports 30 on the shaft 21 are twospaced lands 3| and 32 which, when enclosed by a. sleeve 40, as will belater described, provide between them a chamber 5! for the pressurefluid. Covered by the land 3|. are a series of control ports 41 in thesleeve 40 which are effective in controlling the flow of fluid to andfrom the servomotor. Shaft 21 is provided with a slot 34 which receivesthe key of the ball head l8 and thus establishes a connection for therotation of the ball head 18 by means of the shaft 21.

Supported within the chamber of the dome l2 and between the fly weights22 is an inverted frust'oeconical speeder spring 35. The lower end ofthe spring rests upon a Speeder spring seat 36. The upper part of thespring supports a cup member 31 which provides a shoulder 38 at itslower end. Resting upon the shoulder 38 is the flange 39 0f the pilotvalve sleeve 40. Above the sleeve 4ll isa-ballthrust bearing 4|, thelower race of which rests upon the flange 39 and the upper race of whichengages the toes 25 of the fly ball arms 24. The speeder spring seat 36is preferably equipped with an integral, upwardlyextending sleeve 42which serves to guide the seat 36. Preferably, the sleeve 42 extendsalso slightly belowthe seat 36; The spring seat 36 and sleeve 42 receiveand are guided by a bush- 4 ing 43 which is pressed into-thebore'33'provided in block II, this bushing 43 being one of three (43 and 43)pressed into the bore 33- in spaced relation to one another-to provideannular chambers 45 and 48 around the sleeve in the vicinity ofports-44- and 47.

The pilot valve sleeve 40 is preferably formed of thin metal so that itwill be light and may be moved easily longitudinally of the shaft 2T toprovide an accurate control of the flow of the pressure fluid. It issuspended from the upper spring seat 31 by means of itsflange 39'resting on the shoulder 38 and'moves downwardly in response to pressureexerted upon the ball thrust bearing 41 by the toes- 25 of thefiy'ballarms 24. The sleeve 40 is provided with inlet ports 44 and thecontrol ports 41 previously mentioned. The inlet ports 44 register withthe chamber 45 fed by the fluid conduit 46. The outlet; or' control',ports 41" register with the annular chamber 48 which communicates with aconduit 49 leading to the servomotor chamber 50 (Fig. 4) The ports 4"!cooperate with the land 3! of shaft 21 in controlling the flow of fluidfrom the annular chamber 5| provided. between lands 3|. and 32 and intothe servomotor conduit 49.

For supplying fluid under pressure for the operation of the servomotor,I provide a gear pump which consists of gear 29 on shaft 2T, and'anidler gear 52' meshing with gear 29, as shown in Fig. 2. The gears29 and52,,as shown in Fig. 2', are mounted in recesses provided in the lowerportion of casing block |.l.. Fluid. issupplied to the pump by anysuitable means- Three forms of relief valves are shown in Figs. 3, 3 and3".

In Fig. 3, the block H, or II as the case may be, is provided with areamed diameter hole. H and a reamed diameter hole 51. A ball. 62,spring loaded, as at 64', and held against seat 63, acts as a reliefvalve. Lubricating oil is admitted to the governor from the prime moverlubricating pump through channel 56 in fitting 53. This fluid goesthrough channel 59 to the suction side of the gear pump formed by thegears 29 and 52. This fluid under pressure goes to channel 60. Thespring 64 determines the maximum fluid pressure. If pressure issufficient, the ball 62 is lifted off of the seat 63, allowing the fluidto flow past the ball 62 to the channel 29 as the suction side'of'thegear pump.

Fig. 3 illustrates a second method using a plunger 62 instead of theball 62.

Fig. 3 illustrates a third method. In the illustration given, the blockH is provided with a tapped opening receiving the fitting 53, as shownin. Fig. 3". The fitting 53 is provided with a threaded opening 54adapted to receive a pipe 55, as shown in Fig. 1, said pipe leading toany suitable source of supply, as, for example, the lubricant pump ofthe prime mover. Incoming fluid passes through the opening 56 of thefitting 53 and into the spring chamber 51* provided in the fitting 53 Aport 58 permits: the liquid to flow into the inlet conduit 59, leadingto the inlet sideof the gear pump The gear pump forces the liquid underpressurethrough conduit Bil into the passage 61', which is normallyclosed by the plunger 62 The plunger 62 is urged toward stop pin 63 bythe spring 64. When the pressure of the fluid overcomes the'pressure ofspring 54, the plunger t2 moves, compressing the spring, and uncoversport 65. Fluid is thus-permitted to escape through relief'port 65 and toreturn to the inlet side of the gear pump. By the means described, apredetermined pressure is maintained within the outlet passage of thepump, while at the same time a relief is furnished against excessivepressures. The conduit 46 leads off from the passage 61' to supply fluidto the chamber 51 about shaft 2-1.

It should be obvious that in the event of a reverse direction of drivefor shaft 21; the gearpump, being driven in the opposite direction,makes the passage 60 the inlet and passage- 59 theoutlet, and in suchevent the plug 53 will be entered in hole153, plug 53 being'interchangedwith plug 53*.

The adjustment mechanism varyingthe elevation of the speeder' springseat'36 maybe of any suitableconstruction. Three methods are illustratedin Figs. 2,2 and Fig. 5.

In' the illustration in Fig. 2; I provide an arm 89 which bearsintermediate its end's underv the. spring seat 36', the plunger 83"through the ball. B4, and. the cam. El which is fastened by screws tothe cutaway section of the speed-adjusting shaft 12'. Thespeed-adjusting shaft I2 through the cam. 3|. raises or lowers thespring seat 35 thus changing thespeed Setting. of the governor. With. afixed setting of shaft 12', as: the load on the prime mover increases.the servomotormoves outwardly and the cam 18., due: to the setting: madeby the screw 84-, allowstheplunger 83" to. move. downwardly. This lowersthe ball 88 and the point of contact between arm 89 and the spring seat36', thusgivinga lower speed setting. as. the servomotor 19' movesoutwardly. Thus, we have speed droop and a stable operating; governor.This is the speed droop adjustment. more fully described hereafter byreference to. Figs. 2- and4.

The construction shown in Fig.5 is thesame as illustratedin- Fig. 2:except that the arm Ba is pinned to the plunger 83? by the pin 68.

In.the illustration in Fig. 2", I provide a fork member 66, having itsforked end portion extending around the sleeve 42 and engaging theflange seat 36, as illustrated in Fig. 2'. The rear portion of the fork66 is provided with a boss 61 which is secured by pin 66 to a blockmember 69. The block member 69 is also pivotally mounted upon pin Iwhich secures it to the block II In order to raise or lower the fork 66and thereby the springseat 36, I provide a rotatable cam member II whichhas a cylindrical shaft portion I2 extending outside of the block II, aillustrated in Fig. l, and provided with a slot I3 by means of which theshaft I2 may be rotated. The inner cam portion II may be shaped asillustrated in Fig. 2 and the rotation thereof will elevate fork 66 andthereby the spring seat 36.

I provide special means herein for automatically taking care of speeddroop. Speed droop, which is a decrease in governor speed setting as theservo is opened, is used for stabilization. Mountedwithin the servomotorchamber 50 of easing I I is the servo plunger I4, as illustrated in Fig.4. The plunger I4 is provided with a forked outer end I5 for connectionto a control rod (not shown) connected to a fuel pump. gas mixing valve,steam throttle or other device for controlling the supply of fuel orother energy medium to the prime mover. The plunger- 16 is provided onits lower side with a keyway I6 in which a key 11 extends, the key beingpressed in a hole provided therefor in block II, as illustrated in Fig.l. A cam member I8 is mounted for pivotal movement upwardly anddownwardly upon pin 19 carried on the inner end of plunger I4 and saidcam I8, and is adapted to engage the flattened ball-8ll. The elevationof the cam member I8 is controlled by a threaded pin 8|, having aninwardly-extend ing point engaging the cam and an outwardlyslottedportion 82 adapted to be engaged by a screw driver for inward or outwardadjustment of pin8l. i

The correcting influence of cam I8,;in connection with speed droop, istransmitted through the flattened ball 86 and other mechanism in orderto adjust the speeder spring seat 36. In this mechanism, a plunger 83 isprovided with a rounded seat receiving the upper portion of ball 80 andwith another rounded seat receiving the lower portion of upper ball 84.The upper ball 84 bears against block 69 at a point inwardly from thepivot pin 10, as illustrated in Fig. 2'. Above the block is mounted aleaf spring 34 which maintains a constant downward pressure upon block69, ball B4, and plunger 83, and thus through ball 86 exerts a downwardforce on cam I8. An upward thrust by the cam 18 during the movement ofthe servomotor will cause the ball members 86 and 84, through theplunger 83, to elevate the fork member 66 at a point inwardly from thepivot pin I0, and thus will tilt downwardly the inner end of fork 66 soas to lower the speeder spring seat 36. Likewise, cam I8 may permit alowering of these members which will produce a corresponding rise of thespeeder spring seat 36.

"Shaft 27 is undercut between lands 32and I I9, thus forming a chamberI01. A cross-hole I06 is drilled in shaft 21, and a longitudinal holeI68 of larger diameter than the width of the key 26 is also drilled inshaft 21. Pressure oil will leak over land 32 into chamber I01. This oilwill be forced through holes I06 and I08 into chamber I6, where itserves as a lubricant for the ball head, this oil eventually finding itsWay to chamber 3|] communicating with the sump of the prime mover.

Operation In the operation of the governor, as shown in Figs. 2 and 3,the pressure fluid enters the block II, through the passage 56 infitting 53, as shown in Fig. 3, through chamber 51' to the inlet conduit59 to the gear pump, which will force the fluid through conduit '60 andupwardly into chamber 51 and conduit 6|. If the pressure here becomesexcessive, the ball 62 is forced off the seat 63, against the spring 64,thus allowing the fluid to flow past the ball 62 into the chamber 51 tothe inlet conduit 59 of the gear pump. By this means described, thefluid within the conduit 6| is maintained at the desired pressure andprovides a supply of fluid under pressure to the conduit 46 leading tothe chamber 5 I' provided between the shaft 21 and the pilot valvesleeve 40'. V

In the operation of the governor, as shown in Figs. 2 and 3', thepressure fluid entersthe block I I, through the passage'56 in fitting53, as shown in Fig. 3, through chamber 51f to the inlet con duit 59 tothe gear pump, which will force the fluid through conduit 60 andupwardly into chamber 51 and conduit 6|. If the pressure here becomesexcessive, the plunger 62 is forced off the seat 63, against the spring64, thus allowing the fluid to flow past the plunger 62 into the chamber57, to the inlet conduit 59 of the gear pump. By this means described,the fluid within the conduit 6| is maintained at the desired pressureand provides a supply of fluid under pressure to the conduit 46 leadingto the chamber 5| provided between the shaft 21' and the pilot valvesleeve 40'. V

In the operation of the governor, as shown in Figs. 2' and 3", thepressure fluid enters the block II through passage 56 and port 58, asshown in Fig. 3", to the inlet conduit 59 of the gear pump, which willforce the fluid through outlet conduit 60 and upwardly into conduit 6|.If pressure here becomes excessive, plunger 62 is moved suiflciently touncover port 65, thus allowing the return of pressure fluid to the inletside of the pump. By the means described, the fluid within conduit 6| ismaintained at the desired pressure and provides a supply of fluid underpressure for conduit 46 leading to the chamber 5| provided between shaft21 and pilot valve sleeve 40. I

Shaft 21, which is connected to a driven part of the prime mover,rotates with said driven part and produces a similar rotation of theball head I8, which is suspended upon bearing |'I-. Upon an increase inspeed, the fly weights 22 tend to swing outwardly, and this actioncauses the arms 24, which are rigid with the fly weights 22, to movedownwardly and to press their toes 25 against the upper race of the ballbearing 4|. The downward movement of bearing 4| is resisted by speederspring 35 and causes a corresponding downward movement of pilot valvesleeve 40. As the pilot valve sleeve 40 moves downwardly under thethrust of the fly weights 22, the lower portions of the ports 41 areopened. The servo piston or plunger I4 is externally spring loaded (notshown) so that the spring tends to move the servo plunger inwardly tofuel-off position. The lower portion of the control ports 41 beingopened, allows more oil to flow from the channel or conduit 49 into, thespace between the sleeve and shaft 21, and thus to escape through theattract dump ports-30. The-escape of the pressure fluid gives a lowerfluid pressure on the" servo piston or plunger 14 and the piston' is,therefore, free to yield to the action of the servo pull-back spring.The inward movement of the servo piston or plunger 14 toward thefuel-off position results in a slowing down of the prime mover.

The operation of the governor is exactly in the reverse direction whenthe speed of the prime mover, as reflected by the speed of rotation ofshaft 21, is decreased. In this action, the reduction in centrifugalforce causes the'fly weights 22 to swing inwardly and the" pressureupon'the bearing 4 I is reduced. Speeder spring 35, there fore, raisesthe shoulder 38 and thereby the pilot valve sleeve 40. Upward movementof the sleeve 40 closes the lower portion of the ports 41, thus cuttingoff the flow from channel 49 toward the dumpportsSD; while causing theflow of pressure fluid from the chamber 5| into the servo conduit 49.The increase of pressure fluid in the servo chamber 50 causes the servopiston or plunger 14 to move outwardly and to overcome the pressure ofthe pull-back spring; This movement increases the fuel supplied to theprime mover and thus" the speed of the prime mover increases.

As shown in Fig. 2, the speed setting of the governor is changed byrotating the shaft 12" so that'thecam 9| raises or lowers the arm member89'. The arm member 8 9 in turn exerts pressure against the'seat 35' toincrease or decrease the loading of the speeder spring 35'.

As shown in Fig. 5, the speed setting of the governor is changed byrotating the shaft 12 so that the cam 91- raisesor lowers the arm member89*. The arm member t9 in turn exerts pressure against the seat 36' toincrease or decrease the loading of the speeder spring 35-.

As shown in Fig. 2', the speed setting of the governor is changed byrotating the shaft 12 so that the cam 1i raises or lowers the forkmember 66'. The. fork member 66 in turnexertspressure against the seat36 to increase the loading. of speeder spring 35, or, upon lowering ofthe fork;.to-reduce the loading of the spring 35-.

Withrespect tospeeddroop, if thespeed of the prime mover and thegovernor decreases, then the servo piston or plunger 14 moves outwardly;Assillustrated in Fig. 2, this movementcauses the canrTS', whenthe camis-adjusted to the desired angular position by means of the pin 81", tomove theball members 88' and 84' and the plunger 83.. If the members arelowered, they lower the end of the armBS, thus lowering. the spring seat36 and thus reducing the load on thespeeder spring 35 The opposite orinward movement of the servo. piston or plunger 14' increasestheloadingon the speeder spring 35'.

With respect to speed drool if: the speed oi the prime mover andthegovernordecreaseathen the servo piston or plunger. 14 movesoutwardly. Asillustrated in Fig. 5, this movement. causesthe cam 18,- when the camisadiusted to the desiredangular position by means of the pin 68.,to-movethe ball members. as and 84 and the plunger 83. If the membersare lowered... they lower the end of the arm 89 ,.thus lowering. thespringseat 36' and thus reducing the load on the speeder spring 35'. Theopposite or inwardmovement' of the servo piston or plunger increases theloading on the speeder spring With respect to speed d'roop, i'fthe speedof the prime mover and the governor decreases; then the servo piston orplunger 14' moves outwardly. As illustrated in Fig. 2", this movementcauses cam 1-8, when the cam is adjusted to thedesired n: on

angular position by means of pin 81 to move the ball members and 84- andplunger 83. If the ball members are raised, they move the outer portion61 of the fork B6 upwardly so that the inner end of the fork dropsdownwardly. allows seat 35 to dropand decreases the loading of thespring35'. The opposite movement allows the spring 34 to move the outerportion 51 ct for-k 66 in a downward direction and thus raises theforked end of member 66 and seat 36, whereby the loading of spring 35-is increased.

The effect of the new structure upon dynamic unbalance should bementioned. When oil flows over a land and through a port, a force is setup which tends to close the port opening in prior pilot valvestructures. This force inprior structure is exerted on the land and istransmitted to the speeder spring and fly balls or weights. In my newstructure as above described, the la-nd- IN or 3i, as the case may be,is on the shaft 21 which is held in a fixed vertical position, and thisforce is therefore not transmitted tothe speeder spring- 35 and flyballs 2-2.

The reduction in thickness of the sleeve 40' minimizes the reactionforce transmittedto the fly balls 22 and speeder spring 35'.

Any suitable means for closing theservo chamber 50 may be employed. Inthe illustration given in Fig. 4, the opening of the servo chamber isclosed by a cover 86 secured by four screws 81', or other means, to theblock H.

Itwi-ll be understood that the pilot valve sleeve heretofore describedmay be modified widely. In the illustration given. in Fig. '1, a sleeve40 is employed, having a flange 39 near the top portion thereof adaptedto rest upon the shoulder 38- of the upper spring seat 31. With thisstructure, the tube is equipped with an extension 94' receiving theshaft 21 and lying within the ball bearing 4|.

One difliculty with governors now in use is that with certain primemovers, oscillations of the prime mover will be transmitted to thegovernor, causing an uneven operation of the governor that isobjectionable. To overcome this difficulty, I

havep'rovi'ded a flexible or'resilient' spring drive which will transmitforce from the prime mover to rotate the ball head but will not transmitthe slight oscillations referred to. Such movements areabsorbed in thespring connection and, therefore, do not adversely affect the operation.of the governor;

In the structure shown in Figs. 8 and 9, Iprovide a shaft 95 which issubstantiallyidentical with shaft 21 except that it is provided with alongitudinal channel 96. I employ a spring wire 91 to connect the lowerportion of the shaft 9.5 andan' upper driving head 98.. A hole 99 isdrilled into the lower portion of the shaft 95, and the spring wire 91is made fast Within this hole,.either by a pressed fit, threadedengagement, welding, or other means; Similarly, the upper end of thespring wire 91 is fixed to the shank Hill of the couplerhead 98. Thehead 98 is provided with a narrow slot HJ'I' which is substantially thesame as the slot 34 of shaft 21. The slot 101 opens, however, into aflared slot I92 formed in the upper end portion I03 of the shaft 95, asshown more clearly in Fig. 9. The key 25' on the ball head has oneportion Hi4" fitting closely in slot in I and has two" depending. endportions I05 which have a lost motion fit in the flared slots 1'02. Withthis construction, the head 98 will always drive the ball head Itthrough spring, 91 as long as the spring is effective. Should the spring97 9 break and no longer be sufficient to carry the load from shaft 95to head 98, the key 26 of the ball head I8 will engage its lowerportions H in the flared slot I92 in the upper end I93 of shaft 95 andthus shaft 95 will directly drive by means of slot I02 the key 26 ofball head l8.

With the modified structure shown in Figs.8 and 9, it will be seen thatI have provided a structure which will normally drive the ball head 18only through the resilient spring 91. By this means, any slightirregularities or oscillations of the prime mover will not betransmitted to the ball head but will be absorbed by the resilientmember 9! itself. Should, however, the member 91 break or fail to carrythe load, a direct drive is provided by means of the flared slot I02 inthe upper end of the shaft 95, which slot will engage the key 26 themoment spring 91 becomes ineffective as a driving connection.

While in the foregoing description I have set forth a great variety ofdetails as illustrating preferred embodiments of my invention, it willbe understood that such details may be varied widely by those skilled inthe art without departing from the spirit of my invention.

I claim:

1. In a speed governor adapted for use with a hydraulic servomotor tocontrol the speed of a prime mover, control apparatus comprising a shaftadapted to be rotated by the prime mover and having thereon a pair ofspaced lands, said shaft being held against axial movement, fly weightsmounted on said shaft for rotation thereby, a speeder spring, a slidablevalve tube mounted coaxially with the shaft and supported by the speederspring, said tube being secured against rotation and operative toprovide a chamber between said lands, inlet and outlet ports in saidvalve tube, and means carried by the fly weights for moving said valvetube against the force of said spring operative to vary the relativeposition of one of the lands and the outlet port and thereby to controlthe flow of fluid between the chamber and the servomotor.

2. In a speed governor adapted for use with a hydraulic servomotor tocontrol the speed of a prime mover, control apparatus comprising a shaftadapted to be rotated by the prime mover and having thereon a pair ofspaced lands, said shaft being held against axial movement, fly

weights rotated by said shaft, a speeder spring supported to opposemovement of the fly weights, an axially-slidable valve tube mountedcoaxially with the shaft and providing a fluid chamber between thelands, said tube being suspended from 4 said spring and being providedwith inlet and outlet ports, the outlet port being adapted tocommunicate with the servomotor and to regulate the supply of fluidthereto responsively to relative movement of the valve tube and theshaft.

3. In a speed governor adapted for use with a hydraulic servomotor tocontrol the speed of a prime mover, control apparatus comprising a shaftadapted to be rotated by the prime mover and having thereon a pair ofspaced lands, said shaft being held against axial movement, fly weightsrotated by said shaft, a speeder spring supported to oppose movement ofthe fly weights, a thin, light valve sleeve mounted coaxially with saidshaft and axially slidable thereon, said sleeve forming a fluid chamberbetween the lands and being supported by the speeder spring, meanscarried by the fly weights for moving said sleeve against the force ofsaid speeder spring, and inlet and outlet ports in said valve sleeve,the outlet port being adapted to communicate with the servomotor and toregulate the supply of fluid thereto responsively to relative movementof the valve sleeve and the shaft.

4. In a speed governor adapted for use with a hydraulic servomotor tocontrol the speed of a prime mover, control apparatus comprising a shaftadapted to be rotated by the prime mover and having thereon a pair ofspaced lands, said shaft being held against axial movement, fly weightsmounted for rotation by said shaft, a speeder spring, a valve sleeve inengagement with the speeder spring and mounted coaxially with the shaftand slidable thereon, said sleeve being operative to provide a chamberbetween said lands, an outlet port in said valve sleeve, and means formoving said valve sleeve axially 7 against the force of said speederspring responsively to movement of said fly weights, said axial movementof the sleeve being operative to vary the relative position of theoutlet port and one of the lands.

JOSEPH S. DALE.

REFERENCES CITED The following references are of record in the file ofthis patent:

UNITED STATES PATENTS Number Name Date 1,180,583 Gagg Apr. 25, 19161,600,542 Gagg Sept. 21, 1926 2,142,172 Brill Jan. 3, 1939 2,229,681Sorensen Jan. 28, 1941 2,252,838 Drake Aug. 19, 1941 2,268,230 WarnerDec. 30, 1941 2,270,306 Kalin Jan. 20, 1942 2,292,194 Blymyer Aug. 4,1942 1 2,294,469 Loeffler Sept. 1, 1942 2,364,115 Whitehead Dec. 5, 19442,371,157 Drake Mar. 13, 1945 2,422,966 Hoover June 24, 1947 2,472,050Staples May 31, 1949

